KR101612946B1 - Back lash reducing controling gearing system for helical gear - Google Patents

Abstract

A backlash reduction apparatus for a helical gear including a plurality of input gears will be described. A pair of helical gears formed by combining a doubly-fed input gear and a ring gear, each of which is composed of a plurality of pinion gears meshed along an axis, along an axis; Wherein the engagement of the pair of helical gears includes a engagement structure that engages a ring gear having a different number of teeth, wherein the engagement structure is configured to engage the gear engagement of the ring gear meshing with the doubly- A slip gear for guiding the slip gear to be engaged; And an axial supporting portion for supporting the slip gear in the axial direction, thereby reducing backlash by reducing the interval between the pinion gear and the drive gear.

Description

TECHNICAL FIELD [0001] The present invention relates to a backlash reducing apparatus for a helical gear including a plurality of input gears. BACKGROUND OF THE INVENTION [0002]

The present invention relates to a backlash reducing apparatus for a helical gear including a plurality of input gears, and reduces backlash generated when a helical gear composed of a doubled input gear and a ring gear are engaged with each other.

In combination with gear engagement, a back lash is placed in order to smoothly rotate a pair of gears smoothly. Backlash is a gap between teeth that is required to rotate a pair of rotating gears, and is a gap between teeth when a pair of gears is engaged. The backlash varies depending on the type and characteristics of the gear. Normally, the backlash is designed according to the backlash calculation numerical table so that it is designed according to the design standard. Fig. 1 is a JIS class 0 and class 5 backlash calculation numerical table of a helical gear. Referring to Fig. 1, there is shown a method of obtaining backlash of a JIS class 0 helical gear.

The backlash generated from a pair of driven and driven gear bites reduces the accuracy by varying the theoretical output value and the starting output value depending on the direction of the gear, based on the arc of the gear.

For example, in repeated operations in robots and precision machines, a precision speed reducer is used when the power of the servomotor is insufficient, and helical gears and bevel gears are used to change the power direction. These meshing driven gears control backlash . In practice, ISO and DIN specify the amount of backlash based on the gear grade. In addition, backlash elimination is required even for a precision robot, a machine tool, a servo decelerator, and a split index, and various methods of backlash removal are applied, but the effect is inferior to the cost.

The backlash of the gear is formed by a circumferential direction, a normal direction, an angle, a radius, an axial clearance (not shown), etc. according to the backlash reference in FIG. Calculation of the bite strength, tolerance and output error from backlash can be predicted to some extent.

On the other hand, in order to reduce an output error caused by backlash, gears including a gear to adjust the backlash to small or separate structures have been proposed, but the backlash has not been sufficiently removed. As a method of adjusting the backlash of the gear to a small extent, there is a method of adjusting the center distance of the gear. This can be applied to a helical gear or the like. However, since the center distance of the gear is made small to adjust the clearance in the radial direction to reduce the backlash, there is a problem that the structure for adjusting the center distance becomes complicated.

Fig. 3 is a view showing a construction of a scissors gear for reducing backlash. In this method, a backlash is forcibly pulled by pulling the gear of a counter gear with the force of a spring or the like in a gear in which circumferential backlash is divided into two parts. However, since the gears are bitten when they are pushed in, the lubrication needs to be paid attention so that the oil film is not broken. This method is not suitable for gears with large tooth sliding, and there is a risk of abrupt tooth friction when the oil film is broken at a large sliding surface.

The backlash of the gear has so far been assumed to occur for the potential and the smooth gear rotation. However, it has been difficult to satisfy the cost and the reliability, and the proposal for the backlash removal disclosed in domestic or overseas The use of various materials is required and the processing cost is high.

It is expected that the design of the gear with precise backlash control will enable high precision position control of the total robot position accuracy within the range of about 0.3mm to 0.01mm due to improvement of the robot joint precision. In the CNC control machine tool, It is possible to reduce the use of the encoder, and the cost of operating the machine tool system can be drastically reduced.

Patent Document 1. Korean Patent Application No. 10-2005-0062101

Patent Document 2. Korean Patent Application No. 10-2012-0080568

Patent Document 3. Korean Patent Application No. 10-2011-0107126

Patent Document 4: Korean Patent Application No. 10-2011-0045290

SUMMARY OF THE INVENTION It is an object of the present invention to provide a planetary gear device that includes a pinion gear composed of a helical gear and a plurality of input gears for guiding the drive gear of the ring gear to have a backlash- And to provide a backlash reduction device for a helical gear.

Another object of the present invention is to provide a backlash reducing device for a helical gear including a plurality of input gears for reliably eliminating backlash generated from a helical gear rotating in engagement with a pinion gear at a low cost.

It is still another object of the present invention to provide a backlash reducing device for a helical gear including a plurality of input gears for eliminating backlash of a ring gear on one shaft.

According to the present invention, the above object can be attained by a helical gear comprising: a pair of helical gears formed by combining a doubly-fed input gear and a ring gear, each of which is composed of a plurality of pinion gears, Wherein the engagement of the pair of helical gears includes a engagement structure that engages a ring gear having a different number of teeth, wherein the engagement structure is configured to engage the gear engagement of the ring gear meshing with the doubly- A slip gear for guiding the slip gear to be engaged; And a plurality of pinion gears including a first pinion gear and a second pinion gear for transmitting a rotational force to the ring gear, And the ring gear is composed of a combination of two corresponding helical gears along an axis, one of which is a slip gear engaged with the first pinion gear and rotating about an axis, And a drive gear which receives power input from the first pinion gear and rotates about an axis to drive the shaft, wherein the teeth of the slip gear and the teeth of the drive gear are aligned in parallel, And the axial support of the slip gear is formed with a slide groove Structure for supporting the base axis; A disk inserted in a shaft passing through the ring gear and supported by the base; A thrust bearing spaced apart from the disk and supporting the shaft at the base; And an elastic member for elastically urging the disk between the disk and the thrust bearing with a slip gear, and a plurality of input gears.
Further, according to the embodiment of the present invention, the drive gear is engaged with the shaft by the key and is constrained to the shaft.

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Also, according to an embodiment of the present invention, the axial support of the slip gear comprises: a base structure supporting the shaft; And a thrust bearing which is press-fitted into the base to support and fix the shaft and closely contact the surface of the slip gear to the surface of the drive gear, thereby inducing the friction rotation of the slip gear.

In addition, according to the embodiment of the present invention, since the disk has two or more stoppers along the slide groove of the base on the circumferential surface of the disk, the axial rotation of the disk is restrained in the structure base during the axial rotation, And is brought into close contact with the slip gear.

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According to the embodiment of the present invention, the slip gear includes a frictional portion having a surface on which a surface facing the surface of the drive gear is subjected to a threading operation, or a friction pad, so that the first pinion gear or the drive gear The rotational friction force can be increased when engaged.

Further, according to the embodiment of the present invention, the disk includes a frictional portion having a knurled surface or a friction pad, the surface of which faces the surface of the slip gear, The frictional force can be increased.

According to the embodiment of the present invention, the ring gear is configured such that the tooth surface width of the drive gear is narrower than or equal to the tooth surface width of the slip gear, or the tooth surface width of the slip gear is wider Thereby selectively adjusting the frictional force that varies with the vertical load at which the slip gear contacts the drive gear.

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The backlash reduction apparatus of the helical gear according to the present invention has an effect of guiding gear engagement to zero backlash by reducing the gap between the pinion gear and the ring gear formed of the helical gear.

In addition, the backlash generated in the helical gear which rotates in engagement with the pinion gear, which is a plurality of input gears, is reliably removed.

In addition, since backlash can be reduced through an existing structure-dependent or structure-dependent manner that reduces the backlash of the helical gear, it prevents malfunction and malfunction of the device for backlash removal.

Fig. 1 is a backlash calculation numerical reference chart of gears. Fig.
2 is a backlash reference diagram of a gear.
Fig. 3 is a view of a scissors gear with zero backlash.
4 is a schematic view showing a helical gear engagement state in which a plurality of input gears are combined according to an embodiment of the present invention;
5 is an exploded perspective view showing a backlash reducing apparatus for a helical gear in which a plurality of input gears are combined according to an embodiment of the present invention.
Fig. 6 is an exemplary view of the coupled state of Fig. 5; Fig.
7 is an application example of backlash elimination of a helical gear in which a plurality of input gears are combined according to an embodiment of the present invention.
8 is an exploded perspective view showing a backlash reducing apparatus for a helical gear in which a plurality of input gears are combined according to another embodiment of the present invention.
Fig. 9 is an exemplary view of the coupling state of Fig. 8; Fig.
10 is an application example of backlash elimination of a helical gear in which a plurality of input gears are combined according to another embodiment of the present invention.
FIG. 11A is a view showing a ring gear having a width t of the drive gear tooth surface and a width t1 of the slip gear tooth surface t> t1, according to an embodiment of the present invention, (B) is an example of a ring gear with t = t1, and (c) is a comparative example of a ring gear with t < t1.
12 is an explanatory diagram relating to backlash elimination gear engagement of a helical gear according to an embodiment of the present invention;
Fig. 13 is a calculation formula and a calculation table of the 10t-58t tooth square-shaped potential helical gear of Fig. 12;
Fig. 14 is a calculation formula and a calculation table of the 10t-59t tooth orthogonal method potential helical gear of Fig. 12;
Fig. 15 is a calculation formula and a calculation table of the 10t-60t tooth right angle type potential helical gear of Fig. 12;
Fig. 16 is a calculation formula and a calculation table of the 10t-61t tooth angle-wise method helical gear of Fig. 12;
Fig. 17 is a calculation formula and a calculation table of the 10t-62t tooth rectangular-shaped potential helical gear of Fig. 12;
FIG. 18 is a calculation formula and a calculation table of the 10t-63t tooth angle-wise method helical gear of FIG. 12;

Hereinafter, a configuration of a backlash reduction apparatus for a helical gear including a plurality of input gears according to an embodiment of the present invention will be described with reference to FIGS. 4 to 11. FIG.

4 is a schematic view showing a pair of helical gear teeth engaged with a doubled input gear according to an embodiment of the present invention.

A backlash reduction apparatus for a helical gear including a plurality of input gears according to an embodiment of the present invention is formed of a coupling structure of the double input gear 200 and the ring gear 100 in the engagement of the pair of helical gears G . Referring to FIG. 4, the double input gear 200 is divided into a first pinion gear 210 and a second pinion gear 220.

The present invention is characterized in that a backlash generated when the double input gear 200 comprising the first pinion gear 210 and the second pinion gear 220 having at least two input gears engages the ring gear 100 Reduce.

4, in the backlash reduction apparatus for a helical gear including a plurality of input gears according to the embodiment of the present invention, the ring gear 100 meshing with the doubled input gear 200 includes a shaft 110 And may be two corresponding helical gears coupled together.

The ring gear 100 may be a slip gear 300 that is rotated about the shaft 110 by being engaged with the first pinion gear 210 of the double input gear 200, And is a drive gear (D) that receives power input from the first pinion gear (210) and rotates about the shaft (110) to drive the shaft (110). The slip gear 300 and the drive gear D are arranged side by side in the same direction in the same direction as the teeth of the corresponding helical gear. However, when the number of teeth of the drive gear D is different from the number of teeth of the slip gear 300, the position of the gears may be dislocated due to the difference in the number of teeth. The second pinion gear 220 may be a corresponding helical gear corresponding to the first pinion gear 210.

The double input gear 200 may be a combination of the first pinion gear 210 and the second pinion gear 220 as shown in the figure.

In addition, the double-input gear 200 transmits the input power to the ring gear 100, and includes a driving-speed double pinion gear for deceleration of the speed reducer, a differential-type pinion gear for engaging with the side gear of the car to smooth the turning, A double pinion gear for transmitting the rotational force of the steering wheel to the rack, a double pinion gear for transmitting the rotational force to the engine in the starting motor, a double pinion gear for rotating the upper rotator of the construction machine, , And a double pinion gear for starting and driving the robot.

The ring gear 100 includes means for reducing backlash, which is the interval that occurs at the point where the gear meets.

The means for reducing the backlash includes a drive gear D rotating about the shaft 110 and receiving the rotation input from the first pinion gear 210, which is one of the double-input gears 200, And slip gears 300 that frictionally rotate along the shaft 110 while facing each other.

5 is an exploded perspective view showing a main part of a backlash reducing apparatus for a helical gear including a plurality of input gears according to an embodiment of the present invention.

5, the engagement of a pair of helical gears G engaging along the shaft 110 is transmitted to the teeth of the double input gear 200 and the ring gears 100 .

The pair of helical gears G are connected to the first pinion gear 210 of the double input gear 200 by different numbers of teeth of the drive gear D and the slip gear 300 constituting the ring gear 100, As shown in FIG.

The engaging structure converts the engaging of the drive gear D of the ring gear 100 with the double input gear 200 into a bite reducing backlash which is a gap generated at a point where the teeth of the first pinion gear 210 meet And a slip gear 300.

And an axial support portion 400 for supporting the slip gear 300 in the axial direction. The slip gear 300 having the axial support portion 400 rotates the drive gear D engaged with the first pinion gear 210 which is the double input gear 200 by externally applying a force with frictional force during rotation In the process, push backlash in a direction to reduce backlash.

The double input gear 200 and the ring gear 100 meshing with each other are a helical gear classified into a cylindrical gear and the ring gear 100 is a helical gear divided into a drive gear D and a slip gear 300 Respectively.

In general, helical gears are twisted around the wheel and have helical teeth. The helical teeth appear in either the right angle module or the front module, and thrust is applied to the axial direction when a rotational force is applied to the helical teeth. The spiral teeth are inclined obliquely with a sawtooth line. The relative position of the two axes is parallel to the spur gear but the teeth are inclined so that the thrust is applied in the axial direction. The magnitude of the thrust is the tooth inclination of the helical gear . &Lt; / RTI &gt;

Therefore, when the axial supporting device for coupling the slip gear 300 and the drive gear D to the shaft 110 is provided, the rotational force from the first pinion gear 210 of the double- The slip gear 300 generates a frictional force and reduces backlash, which is a gap between the drive gear and the first pinion gear 210. [

The shaft hole of the slip gear 300 that contacts the outer diameter of the shaft 110 to suppress the excessive slip rotation of the slip gear 300 on the shaft 110 and to induce the friction rotation, The friction member 310 of the shaft 110 may be mounted to induce a shaft friction force on the slip gear 300 contacting the outer diameter of the shaft 110. [ However, it is preferable to apply it in consideration of rotational load of the shaft. As the friction member 310, an elastic member, a brake pad-based material, or a surface-treated member having a rough surface may be appropriately processed and applied, though not shown in the drawings.

Reference numerals 110a and 110b denote 'axes' of the first and second pinion gears, respectively, and reference numeral 120 denotes a 'key groove' in the axis. 150 is a hollow formed in the drive gear.

6 is a perspective view showing gear engagement of a backlash reduction device of a helical gear including a plurality of input gears according to an embodiment of the present invention. 7 is a diagram illustrating an application example of a backlash elimination joint of a helical gear including a plurality of input gears according to an embodiment of the present invention.

4 to 7, the ring gear 100 is a helical gear that meshes with the first pinion gear 210 of the double input gear 200 and is rotated by a slip gear (not shown) And a drive gear D that receives power input from the doubled input gear 200 and rotates about the shaft 110 to drive the shaft 110. [

Here, the slip gear 300 is combined with an axis 110 arranged in parallel to the drive gear D, and receives the rotational force finally transmitted through the first pinion gear 210 to rotate with the drive gear D. The drive gear D and the slip gear 300 are coupled to an axis 110, but are divided. The drive gear D is a drive side gear that rotates the shaft 110.

The slip gear 300 is a helical gear that rotates along the shaft 110 to eliminate backlash generated at a point where the teeth of the drive gear D engaged with the first pinion gear 210 are engaged, The gap between the first pinion gear 210 and the drive gear D is reduced by frictional rotation so that the backlash is removed.

The drive gear D is engaged with the key 130 on the shaft 110 to receive the rotational force from the first pinion gear 210 to drive the shaft 110.

The ring gear 100 composed of the drive gear and the slip gear may be composed of the ring gear 100 having one or more slip gears 300, although not shown in the figure. The figure shows an example in which one slip gear 300 is combined with one drive gear.

The slip gear 300 may be constituted by a ring gear 100 facing either one surface or both surfaces of the drive gear D. [

7, the axial input shaft 200 and the ring gear 100 are helical gears, and the axial thrust force W applied to the shaft 110 during rotation is transmitted to the structure base 500 and the thrust bearing 400a.

The specific structure and operation of the backlash reduction apparatus of the helical gear including the plurality of input gears according to the embodiment of the present invention will be described with reference to FIGS. 4 to 11. FIG.

7, the ring gear 100 is divided into a drive gear D and a slip gear 300. The ring gear 100 is axially supported by a shaft 110, The slip gear 300 may be installed to support the base 500 in the axial direction to induce the friction rotation of the slip gear 300. The shaft 110 to which the thrust W is applied is supported through the structure base 500 and the thrust bearing 400a.

The axial support of the ring gear 100 including the slip gear 300 is supported by the thrust bearing 400a press-fitted into the base 500. [ The thrust bearing 400a is pushed into the base 500 to support and fix the shaft 110 without any flow and is positioned at a position where the surface of the slip gear 300 is brought into close contact with the surface of the drive gear D

The slip gear 300 which is axially supported by the structure base 500 and the thrust bearing 400a is provided with a frictional force due to a helical gear due to the helical gear characteristic and a slip gear contacting the outer diameter of the shaft 110, The frictional force between the inner surface (including the friction member selectively) contact surface and the frictional force between the drive gear and the surface contact surface of the slip gear is added so that the gap generated at the point where the drive gear and the first pinion gear meet, It can be reduced by reaction force.

Here, the frictional force between the drive gear D and the surface contact surface of the slip gear 300 may change the frictional force when the friction portion 320 is placed on the slip gear 300.

8 is an exploded perspective view showing a main part of a backlash reducing apparatus for a helical gear including a plurality of input gears according to an embodiment of the present invention. 9 is a diagram illustrating an example of a combined state of a backlash reduction apparatus for a helical gear including a plurality of input gears according to an embodiment of the present invention. 10 is an exemplary application example of backlash elimination of a helical gear including a plurality of input gears according to another embodiment of the present invention.

As shown in FIGS. 8 to 10, the slip gear 300 is frictionally rotated by driving a ring gear 100, which is divided into a drive gear D and a slip gear 300, And the shaft 110 may be installed to be guided in the axial direction on the structure base 500 and guided.

Specifically, the slide groove 510 is formed in the structure base 500 supporting the shaft 110, the disk 410 is assembled along the slide groove 510, the disk 410 is pushed by the elastic force, Thereby inducing rotational friction of the rotor 300.

The main part includes a structure base 500 for supporting the shaft 110, a disc 410 supported by the base 500 by being inserted in a shaft 110 passing through the ring gear 100, A thrust bearing 400a which is spaced from the disc 410 and supports the shaft 110 to the base 500 and a thrust bearing 400b which is spaced from the thrust bearing 400a by a resilient force to elastically contact the disc 410 with the slip gear 300 between the disc 410 and the thrust bearing 400a Member 430 as shown in FIG. As the elastic member 430, various types of coil springs, leaf springs, and the like can be selectively applied. The figure shows an example of a coil spring.

The disk 410 is coupled to the shaft but is not rotated by the shaft and moves in the axial direction along the slide groove 510 of the base 500 in the elastic force acting direction. The force for applying the pressure to the slip gear 300 is changed according to the elastic force of the elastic member 430, which determines the frictional force acting on the slip gear 300. Therefore, the rotation friction force of the slip gear 300 can be adjusted through the use of the appropriate elastic member 430.

At least two stoppers 410a protrude from the circumferential surface of the disc 410 to engage with the slide groove 510 of the base 500 to restrict axial rotation of the disc and guide the movement of the disc in the axial direction. An elastic force acts on the disk 410 at all times and the disk moves in the direction of the elastic force action and is brought into close contact with the surface of the slip gear 300 with elastic force. As a result, when the slip gear 300 is rotated, a friction force corresponding to the elastic force is generated in the slip gear 300.

The frictional force between the contact surface of the drive gear D and the slip gear 300 and the frictional force between the slip gear 300 and the disk 410 are equal to each other when the friction parts 320 and 420 are placed, The friction force between the contact surfaces can be varied.

However, it is preferable to adjust the frictional force in consideration of the rotational load of the shaft or the drive gear. Although not shown in the drawing, the friction portion 320 may be formed by selectively processing various structures and materials including a brake pad material or a surface processed to have a rough surface, and the like.

The friction portion 320 of the slip gear 300 may be configured to have a knurled surface or a friction pad on a surface facing the surface of the drive gear D. Likewise, in the case of the friction portion 420 of the disk 410, the surface facing the surface of the slip gear 300 can be easily configured with a sliding surface treatment or a friction pad.

It is preferable that the number of teeth T of the drive gear D and the number of teeth T1 of the slip gear 300 constituting the ring gear 100 have a difference of one or more, It is more advantageous to reduce the interval between the teeth of the first pinion gear 210 and the teeth of the drive gear D when the tooth number T1 of the gear is larger than the number of teeth T of the drive gear . In this case, the drive gear and the slip gear are always shifted as shown in the figure.

As described above, the ring gear 100, which is a combination of the drive gear D and the slip gear 300, is engaged with the first pinion gear 210 due to the difference in the number of gear teeth, This misalignment itself acts to narrow the gap between the gears.

The slip gear 300 rotates together with the drive gear D along the shaft 110 and slides on the gear teeth 300 of the slip gear 300 and the gear teeth D of the drive gear D when they are engaged with the first pinion gear 210 This reduces the clearance gap between the gear teeth due to the difference in angular velocity and rotation angle.

FIG. 11A is a view showing a ring gear having a width t of the drive gear tooth surface and a width t1 of the slip gear tooth surface t> t1, according to an embodiment of the present invention, (B) is an example of a ring gear with t = t1, and (c) is a comparative example of a ring gear with t < t1.

(a) is an example of the ring gear 100 in which the tooth surface width t of the drive gear D is combined with a width t> t1, which is relatively wider than the tooth surface width t1 of the slip gear 300 .

5B shows an example of the ring gear 100 in which the tooth surface width t of the drive gear D and the tooth surface width t1 of the slip gear 300 are combined to have the same width t = t1.

(c) shows an example of the ring gear 100 in which the tooth surface width t1 of the slip gear 300 is wider than the tooth surface width t of the drive gear D.

Referring to FIG. 11, it can be seen that the tooth surface width or the thickness of the drive gear and the slip gear of the ring gear can be adjusted by selectively adjusting the tooth surface width as required. The difference in the relative tooth widths of the drive gear and the slip gear may induce a change in thrust and frictional force in the engagement of the pinion gear and the ring gear, which are helical gears having a helical tooth profile.

For example, FIG. 11 (c) shows a case in which the tooth width of the slip gear 300 is relatively wider than that of the drive gear. In this case, the friction induction of the slip gear may be more advantageous than the case without.

FIG. 12 is an explanatory diagram of a backlash elimination of a helical gear including a plurality of input gears according to an embodiment of the present invention, and shows a tooth cross section at a right angle to reduce backlash. Hereinafter, the first pinion gear 210 directly engaged with the drive gear and the slip gear of the ring gear will be described. The description of the second pinion gear 220 is omitted.

12, the number of teeth of the first pinion gear 210 is' 10T ', the number of teeth of the drive gear D engaged therewith is 60T, and the number of teeth of the slip gear 300 of the ring gear 100 is' 63T ', the drive gear D forms a constant engagement ratio with the first pinion gear 210 when the tooth cross-section that reduces backlash is 58T, 59T, 60T, 61T, 62T and 63T. Here, the constant engaging ratio is a reduced backlash, which transmits the rotation of the first pinion gear 210 to the drive gear D and outputs it.

That is, when the number of teeth of the gear except the gear radius is engaged with the gear ratio of 1/6 of the first pinion gear 10T and the drive gear 60T, one rotation of the first pinion gear is transmitted to the drive gear at 1/6 of the rotation amount . The actual engagement ratio of a general helical gear permitting backlash has a value of ± 1/6 due to backlash.

The engagement ratio forms a stable engagement ratio that eliminates backlash such as detail -58T, detail -59T, detail -60T, detail -61T, detail -62T, and detail -63T in FIG. 12. The input side first pinion gear 210, The gear teeth of the slip gear 300 are located at intervals between the gear teeth forming the backlash regardless of the rotational positions of the drive gear D and the slip gear 300 rotating in the same direction It is possible to reduce the gap interval.

12 shows a pair of helical gear engagement states in which the number of teeth of the input side first pinion gear is 10T and the number of teeth of the output side drive gear is 60T and the number of teeth of the slip gear is 63T and the teeth of the drive gear D and the slip gear 300 The backlash generated in the helical gear engagement can be removed by adjusting the distance between the first pinion gear 210 and the electric potential by the difference in the number of teeth.

For example, the number of teeth (T) of the drive gear (D): the number of teeth (T1) of the slip gear (300), when the input first pinion gear teeth number is 10T and the output side drive gear teeth number is 58 to 63T, The number of teeth T of the gear and the number of teeth T1 of the slip gear may have a difference of 1 to 5 ranges. Under these conditions, the number of slip gear teeth can be increased proportionally to the number of teeth of the drive gear, based on the number of teeth of the drive gear, such as one at 58T, and five at 63T.

FIGS. 13 to 18 are diagrams for explaining a design of a potential helical gear for backlash reduction according to an embodiment of the present invention, wherein when the number of teeth of the first pinion gear is 10T and the number of slip gear (ring gear) The number of gear teeth, the tooth angle module, the reference pressure angle, the root gap, and the number of teeth of the slip gear engaged with the helical gear interlocking design are classified into 58T, 59T, 60T, 61T, 62T and 63T, 10T-60T (FIG. 15), 10T-61T (FIG. 16), 10T-62T (FIG. 17), and 10T- 63T (Fig. 18), and is an example of an example of the calculation table.

According to the above example, values are calculated by substituting the tooth angle module, the reference pressure angle, the root gap ratio, and the twist angle except for the number of teeth of the gear teeth in Table 1 below.

Calculation item Output value Right angle module 2 Reference pressure angle 20 Percentage of root gap 0.35 Twist angle 28

Table 2 shows the results obtained by extracting frontal contact pressure angle, end circle diameter, and bite factor that directly affect backlash.

division Front Bite Pressure Angle (°) Diameter of end circle (mm)
Bite rate Pinion Ring gear Pinion Ring gear 10T-58T 0.0343 26.0886 26.289 139.908 1.185 10T-59T 0.0274 24.3109 26.559 139.908 1.269 10T-60T 0.0212 22.4025 26.651 139.908 1.337 10T-61T 0.0157 20.3250 26.553 139.908 1.391 10T-62T 0.0108 18.0210 26.246 139.909 1.435 10T-63T 0.0066 15.3872 25.702 139.908 1.473

According to the tables of FIGS. 13 to 18 and Table 2, the value of the &quot; end circle diameter &quot; of the output side ring gear including the slip gears varying in the number of teeth of the teeth is '139.908' 139.909 '. It can be seen that a value equal or close to the "diameter of the end circle" of the ring gear results in a stable engagement ratio that eliminates the backlash formed by the gap between the input gear (pinion) and the output gear (drive gear) .

A backlash reduction apparatus for a helical gear according to the present invention is a helical gear backlash reduction apparatus for guiding a pinion gear composed of a helical gear to have a bite that narrows a gap generated at a point where a tooth of the drive gear meets, . And since the slip gear for reducing the backlash is integrated into the ring gear, the ring gear can be simply finished with a small processing cost, and the device for backlash elimination is simplified. Further, backlash is easily reduced in a double input gear having one or more input gears.

While the present invention has been particularly shown and described with reference to exemplary embodiments thereof, it is clearly understood that the same is by way of illustration and example only and is not to be taken by way of illustration, .

D: Drive gear G: A pair of helical gears
100: ring gear 110: shaft
120: key groove 130: key
200: doubled input gear 210: first pinion gear
220: second pinion gear 300: slip gear
310: Friction member 320: Friction member
400: Friction rotation inducing means 400a: Thrust bearing
410: Disk 410a: Stopper
420: friction portion 430: elastic member
500: Base 510: Slide groove

Claims (11)

A pair of helical gears formed by combining a doubly-fed input gear and a ring gear, each of which is composed of a plurality of pinion gears meshed along an axis, along an axis; Wherein the engagement of the pair of helical gears includes a engagement structure that engages a ring gear having a different number of teeth, wherein the engagement structure is configured to engage the gear engagement of the ring gear meshing with the doubly- A slip gear for guiding the slip gear to be engaged; And a plurality of pinion gears including a first pinion gear and a second pinion gear for transmitting a rotational force to the ring gear, Gears,
The ring gear comprises a combination of two corresponding helical gears along an axis, one of which is a slip gear meshed with the first pinion gear and rotated about an axis, and the other is a pinion gear And a drive gear which receives the input power and rotates about an axis and drives the shaft by a key on a shaft, wherein the slip gears of the slip gear and the drive gear are arranged in parallel to each other, and the number of teeth of the slip gear is Wherein the axial support of the slip gear comprises: a base structure formed with a slide groove and supporting the shaft; A disk inserted in a shaft passing through the ring gear and supported by the base; A thrust bearing spaced apart from the disk and supporting the shaft at the base; And an elastic member for elastically urging the disk between the disk and the thrust bearing to the slip gear,
A friction member mounted on the shaft hole of the slip gear which contacts the outer diameter of the shaft; And a plurality of input gears including a contact portion between the drive gear and the slip gear, and a friction portion provided between the slip gear and the disk. delete delete delete delete delete The method according to claim 1,
And a plurality of input gears coupled to the circumferential surface of the disk along a slide groove of the base to restrict axial rotation of the disk and induce axial movement of the disk, Device. The method according to claim 1,
Wherein the slip gear includes a plurality of input gears including a friction surface having a surface on which a surface facing the surface of the drive gear is subjected to a threading process or a friction pad. The method according to claim 1,
Wherein the disk includes a plurality of input gears including a friction surface having a surface on which a surface facing the surface of the slip gear is subjected to a threading process or a friction pad. delete The method according to claim 1,
Wherein the ring gear includes a plurality of input gears that are any one of a gear tooth width of the drive gear that is narrower than or equal to a tooth gear width of the slip gear, The backlash reduction device of the helical gear.

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